JP5109992B2

JP5109992B2 - External combustion engine

Info

Publication number: JP5109992B2
Application number: JP2009019382A
Authority: JP
Inventors: 泰徳新山; 金子　　卓; 真一八束; 修三小田; 俊二桶本
Original assignee: Denso Corp
Current assignee: Denso Corp
Priority date: 2009-01-30
Filing date: 2009-01-30
Publication date: 2012-12-26
Anticipated expiration: 2029-01-30
Also published as: JP2010174780A

Description

本発明は、作動媒体の蒸気の体積変動によって生じる作動媒体の液体部分の変位を機械的エネルギに変換して出力する外燃機関に関する。 The present invention relates to an external combustion engine that converts a displacement of a liquid portion of a working medium caused by a change in the volume of vapor of the working medium into mechanical energy and outputs the mechanical energy.

従来、この種の外燃機関が特許文献１、２に記載されている。特許文献１、２の従来技術では、管状の容器内に作動媒体を液体状態で封入し、容器の加熱部で液体状態の作動媒体の一部を加熱して気化させるとともに、その気化した作動媒体の蒸気を容器の冷却部で冷却して液化させることで作動媒体の蒸気の体積変動によって作動媒体の液体部分を液体ピストンとして変位させ、この液体ピストンの変位を機械的エネルギに変換して出力する。 Conventionally, this type of external combustion engine is described in Patent Documents 1 and 2. In the prior arts of Patent Documents 1 and 2, a working medium is sealed in a tubular container in a liquid state, and a part of the working medium in a liquid state is heated and vaporized by a heating unit of the container, and the vaporized working medium The liquid portion of the working medium is displaced as a liquid piston by the volume variation of the working medium vapor, and the liquid piston displacement is converted into mechanical energy and output. .

また特許文献２の従来技術では、管状の容器が加熱部において円盤状に拡径されており、作動媒体の蒸気が冷却部で冷却されて液化すると、液体状態の作動媒体は加熱部の中心部から流入し、加熱部の中心部から外周部に向かって広がって流れる過程で加熱されて再び気化する。 Further, in the prior art of Patent Document 2, the tubular container is expanded in a disk shape in the heating unit, and when the vapor of the working medium is cooled and liquefied by the cooling unit, the working medium in the liquid state is the central part of the heating unit. And is heated and vaporized again in the process of flowing from the central part of the heating part to the outer peripheral part.

この特許文献２の従来技術によると、液体状態の作動媒体が加熱部に流入する際に液体状態の作動媒体が加熱部の内壁面に衝突することとなるので、液体状態の作動媒体が撹拌されて乱流が生じて加熱部の内壁面近傍の温度境界層が破壊される。その結果、加熱部における熱交換効率を向上することができる。 According to the prior art of Patent Document 2, when the liquid working medium flows into the heating unit, the liquid working medium collides with the inner wall surface of the heating unit, so that the liquid working medium is agitated. As a result, turbulent flow occurs and the temperature boundary layer near the inner wall surface of the heating unit is destroyed. As a result, the heat exchange efficiency in the heating part can be improved.

特開２００４−８４５２３号公報JP 2004-84523 A 特開２００７−２４７５９２号公報Japanese Patent Laid-Open No. 2007-247592

本出願人は先に、特願２００８−７２６３号（以下、先願例と言う。）において、加熱部内における作動媒体の流路を微細化したものを提案している。この先願例によると、加熱部内に配置された伝熱部材の内部に、作動媒体が流通可能な微細な流路が多数個形成されており、この伝熱部材によって液体状態の作動媒体の加熱が促進されるので、加熱部で作動媒体を確実に沸騰させて熱損失の低減を図ることができる。 The present applicant has previously proposed a Japanese Patent Application No. 2008-7263 (hereinafter referred to as the prior application example) in which the flow path of the working medium in the heating section is miniaturized. According to this prior application example, a large number of fine flow paths through which the working medium can flow are formed inside the heat transfer member arranged in the heating section, and the heating of the liquid working medium is performed by the heat transfer member. Since it is accelerated | stimulated, a working medium can be reliably boiled in a heating part and reduction of a heat loss can be aimed at.

しかしながら、本発明者の詳細な検討によると、この先願例には効率の低下を招く要因があることがわかった。以下、このことを詳細に説明する。 However, according to a detailed examination by the present inventors, it has been found that there are factors that cause a decrease in efficiency in this prior application. This will be described in detail below.

図８（ａ）は、本発明者が検討した検討例における加熱部の模式的な断面図であり、図８（ｂ）は図８（ａ）の伝熱部材の温度分布を示すグラフである。この検討例は、上記先願例に対応するものである。 FIG. 8A is a schematic cross-sectional view of the heating unit in the study example studied by the present inventor, and FIG. 8B is a graph showing the temperature distribution of the heat transfer member of FIG. . This examination example corresponds to the previous application example.

液体状態の作動媒体１２は、まず図８（ａ）の矢印Ｚ１のように加熱部１１ａの入口側から伝熱部材９０に流入して加熱部１１ａの奥側に向かって流れ、伝熱部材９０で加熱されて沸騰する。すると、作動媒体１２の蒸気は蒸気溜め部９１に溜まった後に膨張して液体状態の作動媒体１２を図８（ａ）の矢印Ｚ２のように加熱部１１ａの奥側から加熱部１１ａの入口側に向かって押し出す。これにより、液体状態の作動媒体１２は伝熱部材９０から加熱部１１ａの入口側に向かって流出する。 The working medium 12 in the liquid state first flows into the heat transfer member 90 from the inlet side of the heating unit 11a and flows toward the back side of the heating unit 11a as indicated by an arrow Z1 in FIG. Heated to boiling. Then, the vapor of the working medium 12 expands after being accumulated in the vapor reservoir 91, and the working medium 12 in a liquid state is moved from the back side of the heating unit 11a to the inlet side of the heating unit 11a as indicated by an arrow Z2 in FIG. Extrude toward Thereby, the working medium 12 in a liquid state flows out from the heat transfer member 90 toward the inlet side of the heating unit 11a.

このことから明らかなように、伝熱部材９０は、加熱部１１ａ入口側に位置する部位ほど液体状態の作動媒体１２との熱交換時間が長時間になる。その結果、図８（ｂ）のように、伝熱部材９０は、加熱部１１ａ入口側に位置する部位ほど温度が低下して、伝熱部材９０に温度分布が生じることとなる。 As is clear from this, in the heat transfer member 90, the heat exchange time with the working medium 12 in the liquid state becomes longer for the portion located on the inlet side of the heating unit 11a. As a result, as shown in FIG. 8B, the temperature of the heat transfer member 90 decreases toward the portion located on the inlet side of the heating unit 11 a, and a temperature distribution is generated in the heat transfer member 90.

図８（ｃ）は、検討例における模式的なＰＶ線図である。図８（ｃ）中、実線は図８（ｂ）のように伝熱部材９０に温度分布が生じているときの状態を示し、図８（ｃ）中、２点鎖線は伝熱部材９０の温度が一様になっている理想的な状態を示している。 FIG. 8C is a schematic PV diagram in the study example. In FIG. 8C, the solid line shows the state when the temperature distribution is generated in the heat transfer member 90 as shown in FIG. 8B, and the two-dot chain line in FIG. It shows an ideal state where the temperature is uniform.

この図８（ｃ）からわかるように、伝熱部材９０に温度分布が生じている場合には、最大圧力が低下してＰＶ出力が低下することとなる。つまり、最大圧力は、伝熱部材９０のうち最も温度の低い部位における温度での飽和蒸気圧とほぼ等しくなることから、伝熱部材９０に温度分布が生じて加熱部１１ａ入口側部位での温度が低下すると最大圧力も低下することとなり、ひいてはＰＶ出力が低下し、効率も低下することとなるのである。 As can be seen from FIG. 8C, when the temperature distribution is generated in the heat transfer member 90, the maximum pressure is lowered and the PV output is lowered. That is, the maximum pressure is substantially equal to the saturated vapor pressure at the lowest temperature portion of the heat transfer member 90, so that a temperature distribution occurs in the heat transfer member 90 and the temperature at the inlet side portion of the heating unit 11a. When the pressure decreases, the maximum pressure also decreases. As a result, the PV output decreases and the efficiency also decreases.

本発明は上記点に鑑みて、効率の向上を図ることを目的とする。 In view of the above points, the present invention aims to improve efficiency.

上記目的を達成するため、請求項１に記載の発明では、作動媒体（１２）が液体状態で流動可能に封入された管状の容器（１１）と、
容器（１１）の一端側部位に形成され、液体状態の作動媒体（１２）の一部を加熱して気化させる加熱部（１１ａ）と、
容器（１１）のうち加熱部（１１ａ）よりも他端側部位に形成され、加熱部（１１ａ）で気化した作動媒体（１２）の蒸気を冷却して液化させる冷却部（１１ｂ）と、
容器（１１）の他端部と連通し、蒸気の体積変動によって生じる液体状態の作動媒体（１２）の変位を機械的エネルギに変換して出力する出力部（１５）とを備え、
加熱部（１１ａ）は、蒸気を溜める蒸気溜め部（２５、４１、５１）を有し、
加熱部（１１ａ）内には、液体状態の作動媒体（１２）の加熱を促進する伝熱部材（２０）が配置され、
伝熱部材（２０）内には、作動媒体（１２）が流通可能な流路（２１）が形成され、
さらに、加熱部（１１ａ）内には、伝熱部材（２０）の温度分布を均一化する温度分布均一化構造が設けられていることを特徴とする。 In order to achieve the above object, in the invention described in claim 1, a tubular container (11) in which a working medium (12) is encapsulated so as to be flowable in a liquid state;
A heating part (11a) that is formed at one end of the container (11) and heats and vaporizes a part of the liquid working medium (12);
A cooling unit (11b) that is formed at the other end side of the heating unit (11a) in the container (11) and that cools and liquefies the vapor of the working medium (12) vaporized by the heating unit (11a);
An output unit (15) that communicates with the other end of the container (11), converts the displacement of the liquid working medium (12) caused by the volume variation of the vapor into mechanical energy, and outputs the mechanical energy;
The heating part (11a) has a steam reservoir part (25, 41, 51) for storing steam,
In the heating part (11a), a heat transfer member ( 20 ) that promotes heating of the liquid working medium (12) is disposed,
A flow path (21) through which the working medium (12) can flow is formed in the heat transfer member ( 20 ),
Furthermore, the heating part (11a) is provided with a temperature distribution uniformizing structure for uniformizing the temperature distribution of the heat transfer member ( 20 ).

これによると、温度分布均一化構造によって伝熱部材（２０、４０、５０）の温度分布が均一化されるので、伝熱部材（２０、４０、５０）の温度分布が大きくなっている場合と比較して、伝熱部材（２０、４０、５０）のうち最も温度の低い部位における温度を上昇させることができる。このため、最大圧力を上昇させてＰＶ出力を向上させることができるので、効率を向上させることができる（図８を参照）。 According to this, since the temperature distribution of the heat transfer member (20, 40, 50) is made uniform by the temperature distribution uniform structure, the temperature distribution of the heat transfer member (20, 40, 50) is increased. In comparison, the temperature of the heat transfer member (20, 40, 50) at the lowest temperature can be increased. For this reason, since the maximum pressure can be raised and the PV output can be improved, the efficiency can be improved (see FIG. 8).

また、請求項１に記載の発明では、温度分布均一化構造は、伝熱部材（２０）に対する液体状態の作動媒体（１２）の供給を均一化する液供給構造で構成されていることを特徴とする。 Moreover, the the invention described in claim 1, temperature distribution uniform structure, which is composed of a liquid supply structure to equalize the supply of the working medium in the liquid state (12) relative to the heat transfer member (20) Features.

これにより、伝熱部材（２０）の各部位における液体状態の作動媒体（１２）との熱交換時間を均一化することができるので、伝熱部材（２０）の温度分布を良好に均一化することができる。 Thereby, since the heat exchange time with the working medium (12) in the liquid state in each part of the heat transfer member (20) can be made uniform, the temperature distribution of the heat transfer member (20) is made uniform uniformly. be able to.

さらに、請求項１に記載の発明では、加熱部（１１ａ）は、容器（１１）を拡径した円盤状に形成されており、
加熱部（１１ａ）内には、伝熱部材（２０）に液体状態の作動媒体（１２）を供給する液供給通路（２３）が形成されており、
液供給構造は、伝熱部材（２０）および液供給通路（２３）が加熱部（１１ａ）の径方向に拡がる形状を有するとともに加熱部（１１ａ）の軸方向に互いに積層されていることによって構成されており、
前記伝熱部材（２０）は、多孔質体で形成され、その内部に形成された細孔によって前記流路（２１）が多数個の微細な流路（２１）として構成されており、
前記蒸気溜め部（２５）は、前記伝熱部材（２０）の径方向外側に前記伝熱部材（２０）と隣接して形成され、前記伝熱部材（２０）内の微細な流路（２１）と直接連通しており、
前記蒸気溜め部（２５）と前記液供給通路（２３）との間には、液体状態の作動媒体（１２）が前記液供給通路（２３）から前記蒸気溜め部（２５）に直接流入することを防止する環状部材（２６）が配置されていることを特徴とする。 Furthermore, in invention of Claim 1 , the heating part (11a) is formed in the disk shape which expanded the container (11),
In the heating part (11a), a liquid supply passage (23) for supplying the working medium (12) in a liquid state to the heat transfer member (20) is formed,
The liquid supply structure is configured by the heat transfer member (20) and the liquid supply passage (23) having a shape that expands in the radial direction of the heating section (11a) and stacked on each other in the axial direction of the heating section (11a). Has been
The heat transfer member (20) is formed of a porous body, and the flow path (21) is configured as a plurality of fine flow paths (21) by pores formed therein,
The steam reservoir (25) is formed on the outer side in the radial direction of the heat transfer member (20) and adjacent to the heat transfer member (20), and a fine flow path (21 in the heat transfer member (20)). )
Between the vapor reservoir (25) and the liquid supply passage (23), the liquid working medium (12) flows directly from the liquid supply passage (23) into the vapor reservoir (25). An annular member (26) for preventing the above is arranged .

これにより、伝熱部材（２０）に対する液体状態の作動媒体（１２）の供給を良好に均一化することができる。 Thereby, the supply of the working medium (12) in the liquid state to the heat transfer member (20) can be made uniform.

なお、この欄および特許請求の範囲で記載した各手段の括弧内の符号は、後述する実施形態に記載の具体的手段との対応関係を示すものである。 In addition, the code | symbol in the bracket | parenthesis of each means described in this column and the claim shows the correspondence with the specific means as described in embodiment mentioned later.

本発明の第１実施形態における外燃機関の概略構成を表す構成図である。It is a block diagram showing schematic structure of the external combustion engine in 1st Embodiment of this invention. （ａ）は図１の加熱部の伝熱部材近傍部位の拡大図であり、（ｂ）は（ａ）の金属粒子の拡大図である。(A) is an enlarged view of the heat transfer member vicinity site | part of the heating part of FIG. 1, (b) is an enlarged view of the metal particle of (a). 図１の加熱部の拡大図である。It is an enlarged view of the heating part of FIG. （ａ）は金属粒子の積層厚さと伝熱部材の上下方向中心部の温度との関係を示すグラフであり、（ｂ）は伝熱部材の上下方向中心部の温度とエンジン効率との関係を示すグラフである。(A) is a graph which shows the relationship between the lamination | stacking thickness of a metal particle, and the temperature of the up-down direction center part of a heat-transfer member, (b) shows the relationship between the temperature of the up-down direction center part of a heat-transfer member, and engine efficiency. It is a graph to show. （ａ）は第２実施形態における加熱部の断面図であり、（ｂ）は（ａ）のＡ−Ａ断面図である。(A) is sectional drawing of the heating part in 2nd Embodiment, (b) is AA sectional drawing of (a). （ａ）は第３実施形態における加熱部の断面図であり、（ｂ）は（ａ）の伝熱部材の粒子径および空隙率の分布を示すグラフである。(A) is sectional drawing of the heating part in 3rd Embodiment, (b) is a graph which shows distribution of the particle diameter and porosity of the heat-transfer member of (a). （ａ）は第４実施形態における加熱部の断面図であり、（ｂ）は（ａ）の伝熱部材の粒子接合直径および見かけの熱伝導率を示すグラフである。(A) is sectional drawing of the heating part in 4th Embodiment, (b) is a graph which shows the particle-joining diameter and apparent thermal conductivity of the heat-transfer member of (a). （ａ）は検討例における加熱部の断面図であり、（ｂ）は（ａ）の加熱部の温度分布を示すグラフであり、（ｃ）は検討例における模式的なＰＶ線図である。(A) is sectional drawing of the heating part in a study example, (b) is a graph which shows the temperature distribution of the heating part of (a), (c) is a typical PV diagram in a study example.

（第１実施形態）
以下、本発明の第１実施形態について図１〜図４に基づいて説明する。図１〜図３中の上矢印は天地方向の上方、下矢印は天地方向の下方を示している。 (First embodiment)
Hereinafter, a first embodiment of the present invention will be described with reference to FIGS. 1 to 3, the up arrow indicates the upside down direction, and the down arrow indicates the upside down direction.

外燃機関１０は、液体ピストン式蒸気エンジンとも呼ばれるものであり、管状の圧力容器である容器１１を備えている。容器１１内には、作動媒体（本実施形態では水）１２が液体状態で流動可能に封入されている。 The external combustion engine 10 is also called a liquid piston steam engine, and includes a container 11 that is a tubular pressure container. A working medium (water in this embodiment) 12 is sealed in the container 11 so as to be able to flow in a liquid state.

また、外燃機関１０は、容器１１内の作動媒体１２の一部を加熱して作動媒体１２の蒸気を発生させる加熱器１３と、加熱器１３によって発生した作動媒体１２の蒸気を冷却する冷却器１４とを備えている。 The external combustion engine 10 also heats a part of the working medium 12 in the container 11 to generate steam of the working medium 12, and cooling to cool the steam of the working medium 12 generated by the heater 13. And a container 14.

本実施形態では、加熱器１３の熱源として排気ガス等の高温ガスを用いている。また、本実施形態の冷却器１４には冷却水が循環するようになっている。図示を省略しているが冷却水の循環回路中には、冷却水が作動媒体１２の蒸気から奪った熱を放熱する放熱器が配置されている。 In the present embodiment, a high-temperature gas such as exhaust gas is used as the heat source of the heater 13. In addition, cooling water circulates in the cooler 14 of the present embodiment. Although not shown in the figure, a radiator that dissipates the heat taken by the cooling water from the steam of the working medium 12 is disposed in the circulating circuit of the cooling water.

容器１１は全体として略Ｕ字形状を有しており、屈曲部が天地方向の最下部に位置し、両端部が天地方向の上方側に向かって延びるように配置されている。この容器１１の一端部に加熱器１３が配置されている。また、容器１１の一端側の部位であって、加熱器１３よりも下方側の部位に冷却器１４が配置されている。 The container 11 has a substantially U-shape as a whole, and is disposed such that the bent portion is positioned at the lowest part in the top-and-bottom direction and both end portions extend upward in the top-and-bottom direction. A heater 13 is disposed at one end of the container 11. In addition, a cooler 14 is disposed at a site on one end side of the container 11 and below the heater 13.

本例では、作動媒体１２を水としていることから、容器１１をステンレス製としている。容器１１のうち加熱器１３と接触する加熱部１１ａおよび冷却器１４と接触する冷却部１１ｂを熱伝導率に優れた銅又はアルミニウム製としてもよい。 In this example, since the working medium 12 is water, the container 11 is made of stainless steel. The heating unit 11a in contact with the heater 13 and the cooling unit 11b in contact with the cooler 14 in the container 11 may be made of copper or aluminum having excellent thermal conductivity.

容器１１の他端部（加熱部１１ａと反対側の端部）には、液体状態の作動媒体１２の変位を機械的エネルギに変換して出力する出力部１５が配置されている。出力部１５は、液体状態の作動媒体１２（液体ピストン）から圧力を受けて変位するピストン（固体ピストン）１６と、ピストン１６を摺動可能に支持するシリンダ部１７を有している。 An output unit 15 that converts the displacement of the liquid working medium 12 into mechanical energy and outputs it is disposed at the other end of the container 11 (the end opposite to the heating unit 11a). The output unit 15 includes a piston (solid piston) 16 that is displaced by receiving pressure from the liquid working medium 12 (liquid piston), and a cylinder unit 17 that slidably supports the piston 16.

ピストン１６は、発電機１の可動子２のシャフト２ａに連結されており、可動子２を挟んでピストン１６と反対側には、可動子２をピストン１６側に押圧する弾性力を発生させる弾性手段をなすバネ１８が設けられている。 The piston 16 is connected to the shaft 2 a of the mover 2 of the generator 1, and an elasticity that generates an elastic force that presses the mover 2 toward the piston 16 on the opposite side of the piston 16 across the mover 2. A spring 18 is provided as a means.

可動子２には永久磁石が埋設されており、ピストン１６が可動子２を振動変位させることによって発電機１を駆動して起電力を発生させる。 A permanent magnet is embedded in the mover 2, and the piston 16 drives the generator 1 by oscillating and moving the mover 2 to generate an electromotive force.

容器１１は加熱部１１ａにおいて水平方向に拡径されている。これに伴い、加熱部１１ａの内部空間も水平方向に拡がる形状になっている。本例では、加熱部１１ａの外形が水平方向に拡がる円盤状になっており、加熱部１１ａの内部空間も水平方向に拡がる円盤形状になっている。図示を省略しているが、本例では加熱部１１ａを適宜分割して形成している。 The container 11 is expanded in the horizontal direction in the heating unit 11a. Along with this, the internal space of the heating unit 11a also has a shape that expands in the horizontal direction. In this example, the outer shape of the heating unit 11a is a disk shape that expands in the horizontal direction, and the internal space of the heating unit 11a is also a disk shape that expands in the horizontal direction. Although illustration is omitted, in this example, the heating part 11a is appropriately divided and formed.

加熱部１１ａの内部空間には、作動媒体１２の加熱を促進する伝熱部材２０が配置されている。図２（ａ）に示すように、伝熱部材２０内には、作動媒体１２が流通可能な流路２１が形成されている。本例では、伝熱部材２０が焼結金属からなる多孔質体で形成されており、この多孔質体の内部に形成された細孔によって多数個の微細な流路２１が構成されている。 A heat transfer member 20 that promotes heating of the working medium 12 is disposed in the internal space of the heating unit 11a. As shown in FIG. 2A, a flow path 21 through which the working medium 12 can flow is formed in the heat transfer member 20. In this example, the heat transfer member 20 is formed of a porous body made of sintered metal, and a large number of fine flow paths 21 are configured by the pores formed inside the porous body.

伝熱部材２０を形成する多孔質体は、伝熱性能が高い金属（本例では、銅）によって球状に形成された金属粒子２２同士をある程度潰して面接合させた構造になっている。球状の粒子２２は、粒度分布が小さい均質な粒子である。本例では、この球状の粒子２２を六方最密構造に充填している。 The porous body forming the heat transfer member 20 has a structure in which metal particles 22 formed in a spherical shape with a metal (copper in this example) having high heat transfer performance are crushed to some extent and are surface-bonded. The spherical particles 22 are homogeneous particles having a small particle size distribution. In this example, the spherical particles 22 are filled in a hexagonal close-packed structure.

なお、図２（ａ）では、図示の都合上、球状の粒子２２同士が点接合しているように示されているが、実際には図２（ｂ）に示すように、球状の粒子２２同士がある程度潰れた状態で面接合している。 In FIG. 2 (a), for convenience of illustration, the spherical particles 22 are shown as being point-joined, but actually, as shown in FIG. 2 (b), the spherical particles 22 are shown. Surface bonding is performed in a state in which they are crushed to some extent.

図３に示すように、伝熱部材２０は、加熱部１１ａの上壁面に沿って配置された第１伝熱部材２０ａ、および加熱部１１ａの下壁面に沿って配置された第２伝熱部材２０ｂで構成されている。 As shown in FIG. 3, the heat transfer member 20 includes a first heat transfer member 20a disposed along the upper wall surface of the heating unit 11a, and a second heat transfer member disposed along the lower wall surface of the heating unit 11a. 20b.

第１、第２伝熱部材２０ａ、２０ｂの間には、加熱部１１ａの径方向に拡がる空隙２３が形成されている。この空隙２３は、第１、第２伝熱部材２０ａ、２０ｂに液体状態の作動媒体１２を供給する液供給通路としての役割を果たすものである。 A gap 23 is formed between the first and second heat transfer members 20a and 20b so as to expand in the radial direction of the heating part 11a. The gap 23 serves as a liquid supply passage for supplying the liquid working medium 12 to the first and second heat transfer members 20a and 20b.

したがって、第１、第２伝熱部材２０ａ、２０ｂおよび液供給通路２３は、いずれも加熱部１１ａの径方向に拡がる形状に形成されているとともに、加熱部１１ａの軸方向に互いに積層されていることとなる。 Accordingly, the first and second heat transfer members 20a, 20b and the liquid supply passage 23 are all formed in a shape that expands in the radial direction of the heating unit 11a, and are stacked on each other in the axial direction of the heating unit 11a. It will be.

加熱部１１ａ内をこのように構成することによって、加熱部１１ａ内には、伝熱部材２０に対する液体状態の作動媒体１２の供給を均一化する液供給構造が設けられることとなる。そして、この液供給構造は、伝熱部材２０の温度分布を均一化する温度分布均一化構造としての役割を果たすこととなる（詳細は後述）。 By configuring the inside of the heating unit 11a in this way, a liquid supply structure that makes the supply of the working medium 12 in a liquid state to the heat transfer member 20 uniform is provided in the heating unit 11a. And this liquid supply structure will play the role of the temperature distribution equalization structure which equalizes the temperature distribution of the heat-transfer member 20 (details are mentioned later).

なお、必ずしも第１、第２伝熱部材２０ａ、２０ｂの両方を加熱部１１ａ内に配置する必要はなく、第１、第２伝熱部材２０ａ、２０ｂのうちいずれか一方のみを加熱部１１ａ内に配置するようにしてもよい。 Note that it is not always necessary to dispose both the first and second heat transfer members 20a and 20b in the heating unit 11a, and only one of the first and second heat transfer members 20a and 20b is in the heating unit 11a. You may make it arrange | position to.

本例では、第１、第２伝熱部材２０ａ、２０ｂおよび液供給通路２３は、加熱部１１ａと同心の円盤状に形成されており、第２伝熱部材２０ｂの中心部には、液供給通路２３に液体状態の作動媒体１２を流通させるための貫通穴が形成されている。 In this example, the first and second heat transfer members 20a, 20b and the liquid supply passage 23 are formed in a disk shape concentric with the heating unit 11a, and a liquid supply is provided at the center of the second heat transfer member 20b. A through hole for allowing the working medium 12 in a liquid state to flow through the passage 23 is formed.

この第２伝熱部材２０ｂの貫通穴の内周面には、加熱部１１ａと同様の材質にて形成された筒状部材２４が配置されている。この筒状部材２４は、液体状態の作動媒体１２が第２伝熱部材２０ｂに対して加熱部１１ａの径方向に流入することを防止する役割を果たすものである。 On the inner peripheral surface of the through hole of the second heat transfer member 20b, a cylindrical member 24 formed of the same material as the heating unit 11a is disposed. The cylindrical member 24 serves to prevent the liquid working medium 12 from flowing in the radial direction of the heating unit 11a with respect to the second heat transfer member 20b.

加熱部１１ａ内において第１、第２伝熱部材２０ａ、２０ｂの径方向外側には、作動媒体１３の蒸気を溜める蒸気溜め部２５が形成されている。この蒸気溜め部２５は、第１、第２伝熱部材２０ａ、２０ｂと隣接して形成されており、第１、第２伝熱部材２０ａ、２０ｂ内の微細流路２１と直接連通している。 In the heating part 11a, a steam reservoir 25 for storing the steam of the working medium 13 is formed on the radially outer side of the first and second heat transfer members 20a, 20b. The vapor reservoir 25 is formed adjacent to the first and second heat transfer members 20a and 20b and directly communicates with the fine flow path 21 in the first and second heat transfer members 20a and 20b. .

蒸気溜め部２５と液供給通路２３との間には、加熱部１１ａと同様の材質にて形成された環状部材２６が配置されている。この環状部材２６は、液体状態の作動媒体１２が液供給通路２３から蒸気溜め部２５に直接流入することを防止する役割を果たすものである。 Between the steam reservoir 25 and the liquid supply passage 23, an annular member 26 formed of the same material as the heating unit 11a is disposed. The annular member 26 serves to prevent the liquid working medium 12 from flowing directly into the vapor reservoir 25 from the liquid supply passage 23.

次に、上記構成における基本作動を簡単に説明する。加熱器１３及び冷却器１４を動作させると、まず加熱器１３により加熱部１１ａ内の作動媒体（水）１２が加熱されて気化し、加熱部１１ａ内に高温・高圧の蒸気が蓄積されて、容器１１の一端側（加熱部１１ａ側）における作動媒体１２の液面１２ａを押し下げる。すると、容器１１内に封入された液体状態の作動媒体１２は、容器１１の一端側から他端側に変位して、発電機１側のピストン１６を押し上げるとともに、バネ１８を圧縮する。 Next, the basic operation in the above configuration will be briefly described. When the heater 13 and the cooler 14 are operated, the working medium (water) 12 in the heating unit 11a is first heated and vaporized by the heater 13, and high-temperature and high-pressure steam is accumulated in the heating unit 11a. The liquid level 12a of the working medium 12 on one end side (heating unit 11a side) of the container 11 is pushed down. Then, the working medium 12 in a liquid state sealed in the container 11 is displaced from one end side to the other end side of the container 11 to push up the piston 16 on the generator 1 side and compress the spring 18.

容器１１の一端側における作動媒体１２の液面１２ａが冷却部１１ｂまで下がり、冷却部１１ｂ内に作動媒体１２の蒸気が進入すると、蒸気が冷却器１４により冷却されて液化されるため、作動媒体１２の液面１２ａを押し下げる力が消滅する。この結果、蒸気の膨張によって一旦押し上げられた発電機１側のピストン１６がバネ１８の弾性力によって下降し、容器１１の一端側において作動媒体１２の液面１２ａが上昇する。 When the liquid surface 12a of the working medium 12 on one end side of the container 11 falls to the cooling unit 11b and the vapor of the working medium 12 enters the cooling unit 11b, the vapor is cooled and liquefied by the cooler 14, and thus the working medium The force that pushes down the liquid level 12a of 12 disappears. As a result, the piston 16 on the generator 1 side once pushed up by the expansion of the steam is lowered by the elastic force of the spring 18, and the liquid surface 12 a of the working medium 12 is raised on one end side of the container 11.

そして、こうした動作は、加熱器１３及び冷却器１４の動作を停止させるまで繰り返し実行され、その間、容器１１内において、液体状態の作動媒体１２は液体ピストンとして周期的に変位（いわゆる自励振動）して発電機１の可動子２を上下動させることになる。 Such an operation is repeatedly executed until the operations of the heater 13 and the cooler 14 are stopped. During this time, the liquid working medium 12 is periodically displaced as a liquid piston in the container 11 (so-called self-excited vibration). Thus, the mover 2 of the generator 1 is moved up and down.

本実施形態では、微細流路２１を有する伝熱部材２０を加熱部１１ａ内に配置しているので、加熱部１１ａに導入された作動媒体１２が微細流路２１内で加熱され沸騰する。このため、温度勾配の影響を排除して作動媒体１２を確実に沸騰（気化）させることができる。しかも、微細流路２１は、球状の粒子２２に囲まれて形成されているので、微細流路２１内で沸騰した蒸気がその周囲の液体状態の作動媒体１２を飛ばしてしまうことを防止できる。 In this embodiment, since the heat transfer member 20 having the fine channel 21 is disposed in the heating unit 11a, the working medium 12 introduced into the heating unit 11a is heated and boiled in the micro channel 21. For this reason, the working medium 12 can be reliably boiled (vaporized) by eliminating the influence of the temperature gradient. In addition, since the fine channel 21 is formed so as to be surrounded by the spherical particles 22, it is possible to prevent the vapor that has boiled in the fine channel 21 from flying the surrounding working medium 12 in the liquid state.

さらに、本実施形態では、伝熱部材２０および液供給通路２３が加熱部１１ａの径方向に拡がる形状を有するとともに加熱部１１ａの軸方向に互いに積層されているので、伝熱部材２０の温度分布を均一化することができ、ひいては効率を向上させることができる。 Furthermore, in this embodiment, since the heat transfer member 20 and the liquid supply passage 23 have a shape that expands in the radial direction of the heating unit 11a and are stacked on each other in the axial direction of the heating unit 11a, the temperature distribution of the heat transfer member 20 Can be made uniform, and as a result, the efficiency can be improved.

このことを詳細に説明すると、図３（ａ）の矢印のように、冷却部１１ｂ側から加熱部１１ａに流入した液体状態の作動媒体１２は液供給通路２３を加熱部１１ａの径方向に拡がって流れて液供給通路２３全体に拡がる。この際、液体状態の作動媒体１２はある程度加熱される。 Explaining this in detail, as shown by the arrow in FIG. 3A, the liquid working medium 12 flowing into the heating section 11a from the cooling section 11b spreads the liquid supply passage 23 in the radial direction of the heating section 11a. Flow and spread over the entire liquid supply passage 23. At this time, the liquid working medium 12 is heated to some extent.

液体状態の作動媒体１２は、液供給通路２３全体に拡がった後、加熱部１１ａの軸方向に流れて第１、第２伝熱部材２０ａ、２０ｂに供給され、第１、第２伝熱部材２０ａ、２０ｂで加熱されて沸騰する。そして、第１、第２伝熱部材２０ａ、２０ｂ内の微細流路２１で発生した蒸気は微細流路２１を蒸気溜め部２５に向かって流れて蒸気溜め部２５に流出し、蒸気溜め部２５に溜まることとなる。 After the working medium 12 in the liquid state spreads over the entire liquid supply passage 23, it flows in the axial direction of the heating unit 11a and is supplied to the first and second heat transfer members 20a and 20b. It is heated by 20a and 20b and boils. Then, the steam generated in the fine flow path 21 in the first and second heat transfer members 20a, 20b flows through the fine flow path 21 toward the vapor reservoir 25, flows out to the vapor reservoir 25, and the vapor reservoir 25. It will be accumulated in.

このように、本実施形態では、伝熱部材２０および液供給通路２３が加熱部１１ａの径方向に拡がる形状を有するとともに加熱部１１ａの軸方向に互いに積層されているので、伝熱部材２０に対する液体状態の作動媒体１２の供給を均一化することができる。 As described above, in the present embodiment, the heat transfer member 20 and the liquid supply passage 23 have a shape that expands in the radial direction of the heating unit 11a and are stacked in the axial direction of the heating unit 11a. The supply of the working medium 12 in the liquid state can be made uniform.

このため、伝熱部材２０と液体状態の作動媒体１２との熱交換時間を伝熱部材２０の入口側部位（径方向内側部位）と奥側部位（径方向外側部位）とで均一化できるので、伝熱部材２０の温度分布を均一化することができる。その結果、伝熱部材２０の温度分布が大きくなっている場合と比較して、伝熱部材２０のうち最も温度の低い部位における温度を上昇させることができる。 For this reason, since the heat exchange time between the heat transfer member 20 and the working medium 12 in the liquid state can be made uniform at the inlet side portion (radially inner portion) and the inner portion (radially outer portion) of the heat transfer member 20. The temperature distribution of the heat transfer member 20 can be made uniform. As a result, compared with the case where the temperature distribution of the heat transfer member 20 is large, it is possible to increase the temperature at the lowest temperature portion of the heat transfer member 20.

ここで、上述のように、ＰＶ線図上の最大圧力は、伝熱部材２０のうち最も温度の低い部位における温度での飽和蒸気圧とほぼ等しくなる。したがって、伝熱部材２０のうち最も温度の低い部位における温度を上昇させることによって最大圧力を上昇させることができるので、ＰＶ出力を向上させることができ、ひいては効率を向上させることができる（図８を参照）。 Here, as described above, the maximum pressure on the PV diagram is substantially equal to the saturated vapor pressure at the temperature of the heat transfer member 20 at the lowest temperature. Therefore, since the maximum pressure can be increased by increasing the temperature at the lowest temperature portion of the heat transfer member 20, the PV output can be improved, and the efficiency can be improved (FIG. 8). See).

次に、伝熱部材２０の一設計例を示す。まず、球状の粒子２２同士の接合面の直径（相当円直径）である接合直径ｄｊ（図２（ｂ）を参照）について説明する。接合直径ｄｊを小さくした場合、すなわち粒子２２同士の潰し量を小さくした場合には、流路２１の断面積の相当円直径（以下、流路径と言う。）が大きくなるので作動媒体１２の流通性が良好である反面、粒子２２間の伝熱面積（接触面積）が小さくなるので伝熱性能が劣る。 Next, one design example of the heat transfer member 20 is shown. First, the joint diameter dj (see FIG. 2B), which is the diameter (equivalent circular diameter) of the joint surfaces of the spherical particles 22 will be described. When the junction diameter dj is reduced, that is, when the amount of crushing between the particles 22 is reduced, the equivalent circular diameter of the cross-sectional area of the flow path 21 (hereinafter referred to as the flow path diameter) increases, and therefore the working medium 12 flows. On the other hand, the heat transfer performance is poor because the heat transfer area (contact area) between the particles 22 is small.

これとは逆に、接合直径ｄｊを大きくした場合、すなわち粒子２２同士の潰し量を大きくした場合には、粒子２２間の伝熱面積が大きくなるので伝熱性能が良好である反面、流路径が小さくなるので作動媒体１２の流通性が劣る。 On the contrary, when the junction diameter dj is increased, that is, when the amount of crushing between the particles 22 is increased, the heat transfer area between the particles 22 is increased, so that the heat transfer performance is good. Therefore, the flowability of the working medium 12 is inferior.

そこで、作動媒体１２の流通性と伝熱性能とを両立するために、接合直径ｄｊを粒子２２の直径ｄの１０％以上、５０％以下にするのが望ましい。より望ましくは、接合直径ｄｊを粒子２２の直径ｄの１／４に設定するのがよい（ｄｊ＝ｄ／４）。 Therefore, in order to achieve both the flowability of the working medium 12 and the heat transfer performance, it is desirable that the joining diameter dj is 10% or more and 50% or less of the diameter d of the particles 22. More preferably, the joining diameter dj is set to ¼ of the diameter d of the particle 22 (dj = d / 4).

なお、ここでいう粒子２２の直径ｄとは、粒子２２のうち、面接合することなく本来の球形状を有している部位で測った直径を意味するものである。 The diameter d of the particle 22 here means the diameter of the particle 22 measured at a portion having an original spherical shape without surface bonding.

次に、粒子２２の積層厚みＬ（図３を参照）について説明する。ここで、粒子２２の積層厚みＬとは、第１、第２伝熱部材２０ａ、２０ｂそれぞれの上下方向寸法のことを意味している。なお、図３では図示の都合上、第２伝熱部材２０ｂにおける粒子２２の積層厚みＬのみを図示しており、第１伝熱部材２０ａにおける粒子２２の積層厚みＬの図示を省略している。 Next, the stacking thickness L of the particles 22 (see FIG. 3) will be described. Here, the lamination thickness L of the particles 22 means the vertical dimension of each of the first and second heat transfer members 20a and 20b. In FIG. 3, for the sake of illustration, only the lamination thickness L of the particles 22 in the second heat transfer member 20b is shown, and the illustration of the lamination thickness L of the particles 22 in the first heat transfer member 20a is omitted. .

第１、第２伝熱部材２０ａ、２０ｂのそれぞれにおける粒子２２の上下方向の積層個数をｎとすると、粒子２２の積層厚みＬは次の数式１のように近似することができる。 When the number of stacked particles 22 in each of the first and second heat transfer members 20a and 20b in the vertical direction is n, the stacked thickness L of the particles 22 can be approximated by the following Equation 1.

（数１）
Ｌ＝ｎｄ
加熱部１１ａの内壁面の温度をＴ１、第１、第２伝熱部材２０ａ、２０ｂの液供給通路２３側端部の温度をＴ２としたとき、球状の粒子２２の伝熱量Ｑｉｎは、次の数式２で表される。 (Equation 1)
L = nd
When the temperature of the inner wall surface of the heating unit 11a is T1, and the temperature of the end portion on the liquid supply passage 23 side of the first and second heat transfer members 20a and 20b is T2, the heat transfer amount Qin of the spherical particles 22 is It is expressed by Formula 2.

但し、λは粒子２２の熱伝導率、Ｓは球状の粒子２２間の伝熱面積（接触面積）である。本例では、ｄｊ＝ｄ／４としているので、球状の粒子２２間の伝熱面積Ｓは次の数式３で表される。

Where λ is the thermal conductivity of the particles 22, and S is the heat transfer area (contact area) between the spherical particles 22. In this example, since dj = d / 4, the heat transfer area S between the spherical particles 22 is expressed by the following Equation 3.

一方、１周期中に球状の粒子２２から流路２１内の作動媒体１２に与えられる熱量Ｑｏｕｔは、次の数式４で表される。

On the other hand, the amount of heat Qout given from the spherical particles 22 to the working medium 12 in the flow channel 21 in one cycle is expressed by the following Equation 4.

（数４）
Ｑｏｕｔ＝Ｖｈ_fgεｆ
但し、Ｖは流路２１内の作動媒体１２の体積であり、ｈ_fgは潜熱であり、εは１周期のうち加熱部１１ａ内に液体状態の作動媒体１２が入っている時間の割合であり、ｆは液体ピストン式蒸気エンジンの駆動周波数である。 (Equation 4)
Qout = Vh _fg εf
Where V is the volume of the working medium 12 in the flow path 21, h _fg is latent heat, and ε is the ratio of the time during which the liquid working medium 12 is in the heating section 11 a in one cycle. , F is the driving frequency of the liquid piston steam engine.

このうち、流路２１内の作動媒体１２の体積Ｖは、次の数式５で表される。 Among these, the volume V of the working medium 12 in the flow path 21 is expressed by the following Equation 5.

但し、ηは伝熱部材２０の空隙率である。

Where η is the porosity of the heat transfer member 20.

そして、次の数式６に示すように、上述の伝熱量Ｑｉｎと熱量Ｑｏｕｔは同じであるから、数１〜数６により次の数式７が導かれる。 Then, as shown in the following formula 6, since the heat transfer amount Qin and the heat amount Qout are the same, the following formula 7 is derived from the formulas 1 to 6.

（数６）
Ｑｉｎ＝Ｑｏｕｔ (Equation 6)
Qin = Qout

図４（ａ）は、この数式７をグラフに表したものであり、粒子２２の積層厚みＬが大きいほど、伝熱部材２０の上下方向中心部の温度Ｔ２が低下することがわかる。なお、図４（ｂ）は、伝熱部材２０の上下方向中心部の温度Ｔ２と液体ピストン式蒸気エンジンの効率との関係を示すグラフである。図４（ｂ）中のＴ３は冷却部１１ｂの内壁面の温度である。

FIG. 4A is a graph of the mathematical formula 7. It can be seen that the temperature T2 at the center in the vertical direction of the heat transfer member 20 decreases as the lamination thickness L of the particles 22 increases. FIG. 4B is a graph showing the relationship between the temperature T2 at the center in the vertical direction of the heat transfer member 20 and the efficiency of the liquid piston steam engine. T3 in FIG.4 (b) is the temperature of the inner wall face of the cooling part 11b.

図４（ｂ）からわかるように、伝熱部材２０の上下方向中心部の温度Ｔ２は、加熱部１１ａの内壁面の温度Ｔ１と冷却部１１ｂの内壁面の温度温度Ｔ３の平均値以上であるのが望ましい。すなわち、伝熱部材２０の軸方向中心部の温度Ｔ２は、次の数式８を満たすのが望ましい。 As can be seen from FIG. 4B, the temperature T2 at the center in the vertical direction of the heat transfer member 20 is equal to or higher than the average value of the temperature T1 of the inner wall surface of the heating unit 11a and the temperature temperature T3 of the inner wall surface of the cooling unit 11b. Is desirable. That is, it is desirable that the temperature T2 at the axial center of the heat transfer member 20 satisfies the following formula 8.

よって、数式７、８により、次の数式９が導かれる。

Therefore, the following Expression 9 is derived from Expressions 7 and 8.

したがって、粒子２２の積層厚みＬがこの数式９を満たすように伝熱部材２０を設計すれば、流路２１内の液相状態の作動媒体１２を良好に蒸発させることができ、液体ピストン式蒸気エンジンを高効率化できる。

Therefore, if the heat transfer member 20 is designed so that the laminated thickness L of the particles 22 satisfies the formula 9, the liquid-phase working medium 12 in the flow path 21 can be vaporized well, and the liquid piston steam The engine can be made highly efficient.

（第２実施形態）
上記第１実施形態では、蒸気溜め部２５が第１、第２伝熱部材２０ａ、２０ｂと隣接して形成されて第１、第２伝熱部材２０ａ、２０ｂ内の微細流路２１と直接連通しているが、本第２実施形態では、図５に示すように、蒸気溜め部２５が第１、第２伝熱部材２０ａ、２０ｂと離間して形成され、かつ第１、第２伝熱部材２０ａ、２０ｂ内の微細流路２１と蒸気通路３０、３１を介して連通している。 (Second Embodiment)
In the first embodiment, the vapor reservoir 25 is formed adjacent to the first and second heat transfer members 20a and 20b and directly communicates with the fine flow path 21 in the first and second heat transfer members 20a and 20b. However, in the second embodiment, as shown in FIG. 5, the vapor reservoir 25 is formed apart from the first and second heat transfer members 20a and 20b, and the first and second heat transfer members are formed. The fine channels 21 in the members 20a and 20b communicate with the vapor passages 30 and 31.

本例では、蒸気通路３０、３１は、第１、第２伝熱部材２０ａ、２０ｂの軸方向外側の端面（本例では、第１伝熱部材２０ａの上端面および第２伝熱部材２０ｂの下端面）から加熱部１１ａの軸方向に延びる複数個の分岐通路部３０ａ、３１ａと、加熱部１１ａの径方向に拡がって複数個の分岐通路部３０ａ、３１ａと連通する集合通路部３０ｂ、３１ｂとで構成されている。 In this example, the steam passages 30 and 31 are end surfaces on the axially outer side of the first and second heat transfer members 20a and 20b (in this example, the upper end surface of the first heat transfer member 20a and the second heat transfer member 20b. A plurality of branch passage portions 30a, 31a extending from the lower end surface in the axial direction of the heating portion 11a, and collecting passage portions 30b, 31b extending in the radial direction of the heating portion 11a and communicating with the plurality of branch passage portions 30a, 31a. It consists of and.

本例では、図５（ｂ）に示すように、複数個の分岐通路部３０ａ、３１ａの断面形状を加熱部１１ａと同心の環状にしている。したがって、加熱部１１ａのうち複数個の分岐通路部３０ａ、３１ａ同士の間の部位は、複数個の環状部３２、３３に分割されることとなる。 In this example, as shown in FIG.5 (b), the cross-sectional shape of several branch channel | path parts 30a and 31a is made into the cyclic | annular form concentric with the heating part 11a. Therefore, the part between several branch channel | path parts 30a and 31a among the heating parts 11a will be divided | segmented into the some cyclic | annular parts 32 and 33. FIG.

複数個の環状部３２、３３は、第１、第２伝熱部材２０ａ、２０ｂを加熱部１１ａに固定するための固定部としての役割と、加熱部１１ａの熱を第１、第２伝熱部材２０ａ、２０ｂに伝えるための伝熱部としての役割を果たしている。 The plurality of annular portions 32 and 33 serve as a fixing portion for fixing the first and second heat transfer members 20a and 20b to the heating portion 11a, and the heat of the heating portion 11a is the first and second heat transfer. It plays a role as a heat transfer part for transmitting to the members 20a and 20b.

本例では、図示を省略しているが、集合通路部３０ｂ、３１ｂの平面形状を加熱部１１ａと同心の円形状にしている。また、図示を省略しているが、加熱部１１ａには、集合通路部３０ｂ、３１ｂ内にて上下方向に延びる柱状部が形成されている。 In this example, although not shown, the planar shapes of the collecting passage portions 30b and 31b are concentric with the heating portion 11a. Although not shown, the heating portion 11a is formed with columnar portions extending in the vertical direction in the collecting passage portions 30b and 31b.

集合通路部３０ｂ内の柱状部は、複数個に分割された環状部３２を、加熱部１１ａのうち集合通路部３０ｂよりも上方側の部位と繋ぐ役割を果たすものである。同様に、集合通路部３１ｂ内の柱状部は、複数個に分割された環状部３３を、加熱部１１ａのうち集合通路部３１ｂよりも下方側の部位と繋ぐ役割を果たしている。 The columnar part in the collective passage part 30b plays a role of connecting the annular part 32 divided into a plurality of parts to a part above the collective passage part 30b in the heating part 11a. Similarly, the columnar part in the collective passage part 31b plays a role of connecting the annular part 33 divided into a plurality of parts to the lower part of the heating part 11a than the collective passage part 31b.

本例では、図示を省略しているが、蒸気溜め部２５を加熱部１１ａの周方向の全域にわたって形成し、蒸気溜め部２５の断面形状を加熱部１１ａと同心の円筒状にしている。なお、必ずしも蒸気溜め部２５を加熱部１１ａの周方向の全域にわたって形成する必要はなく、例えば蒸気溜め部２５を加熱部１１ａの周方向の一部のみに形成し、蒸気溜め部２５の断面形状を円弧状にしてもよい。 In this example, although not shown, the vapor reservoir 25 is formed over the entire area in the circumferential direction of the heating unit 11a, and the cross-sectional shape of the vapor reservoir 25 is concentric with the heating unit 11a. It is not always necessary to form the vapor reservoir 25 over the entire area in the circumferential direction of the heating unit 11a. For example, the vapor reservoir 25 is formed only in a part of the circumferential direction of the heating unit 11a. May be arcuate.

本実施形態によると、第１、第２伝熱部材２０ａ、２０ｂ内の微細流路２１で発生した蒸気は、第１、第２伝熱部材２０ａ、２０ｂの軸方向外側の端面に略均等に配置された蒸気通路３０、３１を通って蒸気溜め部２５に溜まることとなる。 According to the present embodiment, the steam generated in the fine flow path 21 in the first and second heat transfer members 20a and 20b is substantially evenly distributed on the end surfaces of the first and second heat transfer members 20a and 20b on the outer side in the axial direction. It will accumulate in the steam reservoir 25 through the disposed steam passages 30 and 31.

このため、上記第１実施形態と比較して、第１、第２伝熱部材２０ａ、２０ｂ内の各部位において液体状態の作動媒体１２の流れを均一化できるので、第１、第２伝熱部材２０ａ、２０ｂ内の各部位を流れる液体状態の作動媒体１２の流量を均一化できる。その結果、伝熱部材２０の温度分布をより均一化することができる。 For this reason, compared to the first embodiment, the flow of the working medium 12 in the liquid state can be made uniform in each part in the first and second heat transfer members 20a and 20b, so the first and second heat transfer The flow rate of the working medium 12 in the liquid state flowing through the respective parts in the members 20a and 20b can be made uniform. As a result, the temperature distribution of the heat transfer member 20 can be made more uniform.

（第３実施形態）
上記第１実施形態では、伝熱部材２０に対する液体状態の作動媒体１２の供給を均一化する液供給構造によって、伝熱部材２０の温度分布を均一化する温度分布均一化構造を構成しているが、本第３実施形態では、伝熱部材４０の熱容量を加熱部１１ａ入口側に向かうほど増大させる熱容量増大構造によって当該温度分布均一化構造を構成している。 (Third embodiment)
In the said 1st Embodiment, the temperature distribution equalization structure which equalizes the temperature distribution of the heat-transfer member 20 is comprised by the liquid supply structure which equalizes the supply of the working medium 12 of the liquid state with respect to the heat-transfer member 20. FIG. However, in the third embodiment, the temperature distribution uniform structure is configured by a heat capacity increasing structure that increases the heat capacity of the heat transfer member 40 toward the inlet side of the heating unit 11a.

本実施形態では、図６（ａ）に示すように、伝熱部材４０は、加熱部１１ａ内に一体的に配置されている。したがって、蒸気溜め部４１は加熱部１１ａの内部空間のうち径方向最外側部位のみに形成されている。 In this embodiment, as shown to Fig.6 (a), the heat-transfer member 40 is arrange | positioned integrally in the heating part 11a. Therefore, the vapor reservoir 41 is formed only in the radially outermost portion of the internal space of the heating unit 11a.

そして、図６（ｂ）に示すように、伝熱部材４０内の空隙率が加熱部１１ａ入口側に向かうほど減少するように伝熱部材４０が形成されている。これにより、伝熱部材４０の熱容量を加熱部１１ａ入口側に向かうほど増大させている。 And as shown in FIG.6 (b), the heat-transfer member 40 is formed so that the porosity in the heat-transfer member 40 may decrease, so that it goes to the heating part 11a entrance side. Thereby, the heat capacity of the heat transfer member 40 is increased toward the inlet side of the heating unit 11a.

つまり、伝熱部材４０と液体状態の作動媒体１２との熱交換時間が加熱部１１ａ入口側に向かうほど長くなることに鑑みて、伝熱部材４０の熱容量を、当該熱交換時間の分布と同様に、加熱部１１ａ入口側に向かうほど増大させている。 That is, in view of the fact that the heat exchange time between the heat transfer member 40 and the liquid working medium 12 increases toward the inlet side of the heating unit 11a, the heat capacity of the heat transfer member 40 is the same as the distribution of the heat exchange time. In addition, it is increased toward the inlet side of the heating unit 11a.

このため、伝熱部材４０のうち加熱部１１ａ入口側部位における温度低下を抑制することができるので、上記第１実施形態と同様に、伝熱部材４０の温度分布を均一化することができる。 For this reason, since the temperature fall in the heating part 11a entrance side site | part can be suppressed among the heat transfer members 40, the temperature distribution of the heat transfer member 40 can be equalize | homogenized similarly to the said 1st Embodiment.

より好ましくは、伝熱部材４０の空隙率が液体状態の作動媒体１２との熱交換時間に反比例していれば、伝熱部材４０の熱容量が当該熱交換時間に比例することとなるので、伝熱部材４０の温度分布をより均一化できる。 More preferably, if the porosity of the heat transfer member 40 is inversely proportional to the heat exchange time with the liquid working medium 12, the heat capacity of the heat transfer member 40 is proportional to the heat exchange time. The temperature distribution of the heat member 40 can be made more uniform.

（第４実施形態）
上記第３実施形態では、伝熱部材４０の熱容量を加熱部１１ａ入口側に向かうほど増大させる熱容量増大構造によって、伝熱部材４０の温度分布を均一化する温度分布均一化構造を構成しているが、本第５実施形態では、図７に示すように、伝熱部材５０の見かけの熱伝導率を加熱部１１ａ入口側に向かうほど増大させる熱伝導促進構造によって当該温度分布均一化構造を構成している。 (Fourth embodiment)
In the said 3rd Embodiment, the temperature distribution equalization structure which equalizes the temperature distribution of the heat-transfer member 40 is comprised by the heat capacity increase structure which increases the heat capacity of the heat-transfer member 40 so that it goes to the heating part 11a entrance side. However, in the fifth embodiment, as shown in FIG. 7, the temperature distribution uniformization structure is configured by a heat conduction promotion structure that increases the apparent heat conductivity of the heat transfer member 50 toward the inlet side of the heating unit 11a. is doing.

本実施形態では、上記第３実施形態と同様に、伝熱部材５０は、加熱部１１ａ内に一体的に配置されている。したがって、蒸気溜め部５１は加熱部１１ａの内部空間のうち径方向最外側部位のみに形成されている。 In the present embodiment, as in the third embodiment, the heat transfer member 50 is integrally disposed in the heating unit 11a. Therefore, the vapor reservoir 51 is formed only in the radially outermost portion of the internal space of the heating unit 11a.

そして、伝熱部材５０を形成する金属粒子同士の接合直径（図２（ｂ）を参照）を加熱部１１ａの入口側に向かうほど大きくすることによって、伝熱部材５０の見かけの熱伝導率を加熱部１１ａ入口側に向かうほど増大させる熱伝導促進構造を構成している。 And the apparent thermal conductivity of the heat transfer member 50 is increased by increasing the joint diameter (see FIG. 2B) of the metal particles forming the heat transfer member 50 toward the inlet side of the heating unit 11a. The heat conduction promoting structure is configured to increase toward the inlet side of the heating unit 11a.

つまり、金属粒子の接合直径を大きくするほど伝熱部材５０内部の伝熱量が増加するので、伝熱部材５０のうち加熱部１１ａ壁面から離れた部位（図７（ｂ）の例では、上下方向中心部）まで加熱部１１ａからもらった熱を良好に伝えることができる。このため、金属粒子の接合直径を大きくするほど、伝熱部材５０の見かけの熱伝導率が増大することとなる。 That is, since the amount of heat transfer inside the heat transfer member 50 increases as the joining diameter of the metal particles increases, the portion of the heat transfer member 50 away from the wall surface of the heating unit 11a (in the example of FIG. 7B, the vertical direction). The heat obtained from the heating part 11a can be transmitted well to the center part). For this reason, the apparent thermal conductivity of the heat transfer member 50 increases as the bonding diameter of the metal particles increases.

本実施形態によると、伝熱部材５０の見かけの熱伝導率を加熱部１１ａ入口側に向かうほど増大させているので、伝熱部材５０のうち加熱部１１ａ入口側部位における温度低下を抑制することができる。このため、上記第３実施形態と同様に、伝熱部材５０の温度分布を均一化することができる。 According to the present embodiment, the apparent thermal conductivity of the heat transfer member 50 is increased toward the inlet of the heating unit 11a, so that the temperature decrease in the heating unit 11a inlet side portion of the heat transfer member 50 is suppressed. Can do. For this reason, similarly to the said 3rd Embodiment, the temperature distribution of the heat-transfer member 50 can be equalize | homogenized.

より好ましくは、伝熱部材５０の見かけの熱伝導率が当該熱交換時間に比例するように金属粒子同士の接合直径を設定すれば、伝熱部材５０の温度分布をより均一化できる。 More preferably, the temperature distribution of the heat transfer member 50 can be made more uniform if the joining diameter of the metal particles is set so that the apparent thermal conductivity of the heat transfer member 50 is proportional to the heat exchange time.

（他の実施形態）
（１）上記各実施形態は、加熱部１１ａの内部空間の平面形状の一例を示したものに過ぎず、これに限定されることなく、加熱部１１ａの内部空間の平面形状を種々変更可能である。 (Other embodiments)
(1) Each said embodiment is only what showed an example of the plane shape of the internal space of the heating part 11a, It is not limited to this, The plane shape of the internal space of the heating part 11a can be variously changed. is there.

（２）上記各実施形態では、加熱器１３と容器１１とを別体に形成しているが、加熱器１３と容器１１のうち加熱部１１ａとを一体に形成してもよい。 (2) In each of the above embodiments, the heater 13 and the container 11 are formed separately, but the heating unit 11a of the heater 13 and the container 11 may be integrally formed.

（３）上記各実施形態では、加熱器１３の熱源として高温ガスを用いているが、加熱器１３を電気ヒータで構成してもよい。 (3) In each said embodiment, although high temperature gas is used as a heat source of the heater 13, you may comprise the heater 13 with an electric heater.

（４）上記各実施形態では、本発明を発電装置の駆動源に適用した場合について説明したが、本発明の外燃機関は、発電装置以外の駆動源としても利用することができる。 (4) In each of the above embodiments, the case where the present invention is applied to the drive source of the power generation apparatus has been described. However, the external combustion engine of the present invention can also be used as a drive source other than the power generation apparatus.

（５）上記各実施形態では、容器１１が加熱部１１ａにおいて水平方向に拡径されており、加熱部１１ａが水平方向に拡がる円盤状になっているが、これに限定されるものではなく、例えば容器１１が水平方向に拡径されておらず、加熱部１１ａが上下方向に直線状に延びる管状になっていてもよい。 (5) In each of the embodiments described above, the diameter of the container 11 is expanded in the horizontal direction in the heating unit 11a, and the heating unit 11a has a disk shape that expands in the horizontal direction, but is not limited thereto. For example, the diameter of the container 11 may not be expanded in the horizontal direction, and the heating unit 11a may have a tubular shape that extends linearly in the vertical direction.

（６）上記各実施形態では、作動媒体として水を用いているが、これに限定されるものではなく、例えば作動媒体として冷媒を用いてもよい。 (6) In each of the above embodiments, water is used as the working medium. However, the present invention is not limited to this. For example, a refrigerant may be used as the working medium.

１１容器
１１ａ加熱部
１２作動媒体
２０伝熱部材
２３液供給通路
２５蒸気溜め部 DESCRIPTION OF SYMBOLS 11 Container 11a Heating part 12 Working medium 20 Heat-transfer member 23 Liquid supply path 25 Steam reservoir

Claims

A tubular container (11) in which a working medium (12) is encapsulated so as to be able to flow in a liquid state;
A heating unit (11a) that is formed at one end portion of the container (11) and heats and vaporizes a part of the liquid working medium (12);
A cooling part (11b) that is formed in the container (11) at the other end side than the heating part (11a) and cools and liquefies the vapor of the working medium (12) vaporized by the heating part (11a). )When,
An output unit (15) that communicates with the other end of the container (11) and converts the displacement of the working medium (12) in the liquid state caused by the volume variation of the vapor into mechanical energy and outputs the mechanical energy; ,
The heating part (11a) has a steam reservoir part (25, 41, 51) for storing the steam,
In the heating part (11a), a heat transfer member ( 20 ) for promoting the heating of the working medium (12) in the liquid state is disposed,
The heat transfer member ( 20 ) is formed with a flow path (21) through which the working medium (12) can flow.
Furthermore, in the heating unit (11a) is an external combustion engine provided with a temperature distribution uniform structure for homogenizing the temperature distribution of the heat transfer member ( 20 ) ,
The temperature distribution uniform structure is configured by a liquid supply structure that uniformizes the supply of the liquid working medium (12) to the heat transfer member (20),
The heating part (11a) is formed in a disk shape having an enlarged diameter of the container (11),
A liquid supply passage (23) for supplying the working medium (12) in the liquid state to the heat transfer member (20) is formed in the heating unit (11a).
The liquid supply structure has a shape in which the heat transfer member (20) and the liquid supply passage (23) extend in the radial direction of the heating section (11a) and are stacked on each other in the axial direction of the heating section (11a). Is made up of
The heat transfer member (20) is formed of a porous body, and the flow path (21) is configured as a plurality of fine flow paths (21) by pores formed therein,
The steam reservoir (25) is formed on the outer side in the radial direction of the heat transfer member (20) and adjacent to the heat transfer member (20), and a fine flow path (21 in the heat transfer member (20)). )
Between the vapor reservoir (25) and the liquid supply passage (23), the liquid working medium (12) flows directly from the liquid supply passage (23) into the vapor reservoir (25). An external combustion engine characterized in that an annular member (26) for preventing the above is disposed .